Liquid dispenser



O. H. DUDA LIQUID DISPENSER Jan. l9, 1968 Filed March 1, 196e UnitedStates Patent 3,362,343 LIQUID DISPENSER Otto H. Duda, Hacienda Heights,Calif., assigner to Calmar, Inc., City of Industry, Calif., acorporation of California Filed Mar. 1, 1966, Ser. No. 530,855 16Claims. (Cl. 103-178) This invention relates to improvements in liquiddispensing pumps of the type generally disclosed in the Corsette PatentNo. 3,228,347, of common ownership herewith.

The aforesaid application disclosed dispensing pumps adapted forapplication to portable containers in which various liquid products aresold and in which the pumps are particularly adapted for application tothe -lilled containers at the factory to 4be sulbsequently sh-ipped withthe lled containers to suitable sources of distribution.

It is particularly important, therefore, that such dispensers beequipped with suita'ble shipping seals adapted for preventing leakage ofthe liquid, either through the pump discharge passages or between thepump cylinder and plunger, incident to rough handling or inversion ofthe containers. It is also desirable that such shipping lseals ybeeffec-tive in either the fully-projected or the fullydepressed positionof the plunger so that the same basic pump structure may 4be shippedwith the plunger in either position, except that where the pump and itsassociated container are to be shipped with the plunger in itsfullyprojected position, the usual means for locking it in afully-depressed position may be omitted.

It is an object of the invention to render a reciprocating pump typedispenser capalble of achieving the foregoing ends and also to adapt ityfor economical production and assembly. Also, it is an important objectof the present invention to provide an improved pump structure capableof attaining the foregoing ends by means of a relatively-reduced numberof parts, and also capable of other important advantages.

-In accordance with the present invention, there is provided africti-onal coupling or telesc-oping clutch connection between theplunger and the inlet valve stem. This connection is rendered operativeonly near the extremity of the plunger retraction movement (on itssuction stroke) to transmit a seating force to the inlet valve uponinception of the next-ensuing compression stroke of the plunger. Suchfrictional coupling is established by frictional reception of anenlargement of the valve stem in a constricted portion of the plungerdischarge passage.

It is a yfurther important feature of the invention to make dualutilization of the said clutch structure, both for clutching purposesand also as a sealing valve which is automatically closed and openincident to the engagement and disengagement of the clutch, thus toautomatically establish a shipping seal in the fully-projected plungerposition.

Further, there is provided an additional frictional connection orcoupling between the plunger and inlet valve, established only as theplunger nears its fully-depressed position. This coupling, which isestab-lished incident to the complete depressing Iof the plunger,opera-tes to exert an unseating force on the pump inlet valve on theinception of the next suction stroke of the plunger and is automaticallydiscontinued after but a brief projection movement of the plunger inorder to -avoid interference with the continued plunger movement.

It is a further feature of the invention that this additional frictionalconnection also may serve the function of a sealing valve or plugoperative in the fully depressed position of the plunger.

Thus, where -both of the dual-acting frictional cou- Patented Jan, 9,1968 plings and sealing valves are employed, the inlet valve is bothseated and unseated by movement of the plunger from either extremity ofits movement; and, in addition, the plunger discharge passage iseffectively sealed when the plunger is at either extremity of itsmovement.

Moreover, there is contemplated an advantageous disposition of thesealing valve for relative movement between axially-sp'aced por-ts inthe discharge passage of the plunger, incident to reciprocation of thelatter, and for alternate seat-ing Irelative to these ports at oppositeextremities of the plunger movement, to thus provide effective shippingseals at either extremity of the plunger movement.

In accordance with certain specific but advantageous 4features of theinvention, the sealing valve is so associated with one of its saidsealing ports yas to be capable of ybeing forced there-through to anoperative position between the alternate ports, thus facilitatingassembly of these parts. Also, provision is made for simultaneouslyseating of the inlet valve and the sealing valve by direct engagementbetween the sealing valve and a plunger seat or port in thefully-depressed position of the plunger and for maintenance of aconstant resilient seating pressure of both of these valves with `theirassociated ports by forming either or both of the valve seats aroundsaid ports of elastically expansible material, to be expanded by seatingtherein of conical portions of the sealing and/or inlet valves.

The invention also provides an improved external seal (that is, a sealexternally of the plunger between the plunger and -cylinderl in whichthe seal is rendered operative only at the extremity of the plungermovement and is rendered inoperative throughout the major portion of theplunger stroke in either direction, -both to avoid impeding the plungerstroke and also to establish communication of the container interiorwith the exterior atmosphere so as to permit the entry of air to takethe place of liquid removed by the pump.

To this end, the invention employs a novel arrangement of sealing ringor gasket which encircles the plunger rod and is interposed between ytheplunger rod and cylinder. The plunger rod is formed to cooperate withthe said sealing ring in lthe manner of a slide valve and, for thispurpose, is formed with suitably-positi-oned enlargements adapted toenter the sealing ring, preferably at fboth extremities of the plungermovement, so as to compress the ring radially between the opposed Wallportions of the cylinder and plunger. Between such enlargements, theplunger rod is Ifo-rmed to permit a suicient flow or seepage of air forventing purposes.

A preferred embodiment of the invention, incorporating the variousfeatures and advantages above enumerrated, is illustrated -by way ofexemplication in the accompanying drawings in which:

FIGURE l is a sectional view in an axial plane through a reciprocatingpump structure in accordance Iwith the invention wherein said structureis supported in a heretofore-known manner in a container closure. Inthis figure, the plunger of the pump is in its fully-projected position;

FIGURE 2 is a view similar to FIGURE l, but with the plunger secured inits fully-depressed position; and

FIGURE 3 is a section on the line 3--3 of FIGURE l showing certaindetails of the inlet valve construction.

The accompanying drawings and the ensuing detailed description are lbyWay of exemplication only for the purpose of disclosing what is-presently contemplated as 'the best mode of practicing the invention.It will accordingly be understood that the description and accompanyingdrawings both will involve details which may be omitted or changed, asthose skilled in the art will understand, without departing from thespirit of the invention.

Referring now in detail to the structure shown in the accompanyingdrawing, same illustrates a reciprocating pump in which the severalelements or components, broadly speaking-cooperate in conventionalmanner to achieve the pumping action, and, in addition, incorporatecertain new structural features, advantages and modes of cooperation aslater described.

Considering first the general organization of elements, the pumpstructure is adapted to be supported in the outlet of a liquid containerto dispense the contents thereof. Accordingly, the pump cylinder 10,which is here exemplified as the stationary portion of the pump, isprovided with a conventional fianged collar 12 at its upper end. Thiscollar 12 extends through and supports the pump cylinder within anopening defined by the top wall 13 of a container closure, hereillustrate-d as provided with a depending internally-threaded skirt 144for application in usual manner to the externally-threaded neck orspout of a bottle or other usual container, not here illustrated. Theupper and lower fianges 16 and 17 respectively of the collar 12 projectabove and below the closure top wallr13 to secure the collar in placewithin the central opening lof the closure wall 13, the upper flange 16being formed, preferably Iby a swaging action in known manner, after thecollar has been inserted through the opening to bring the pre-formedflange 17 into abutment with the lower surface of the top wall. It willbe apparent that the threading of the closure 13 onto the container willclamp to the lower fiange 17 against the upper end of the container neckor spout. The annular sealing rib 1S of the lower flange exemplifies anyconventional means for providing fluid-tight engagement of the flange 17with the bottle neck.

It will thus be seen that the major portion of the pump cylinder 10, aswell as of the pump in its entirety, will normally be housed within thecontainer with its lower end communicating with the container contentsthrough an axially-directed inlet port 20 which, in the preferredembodiment, is defined by the elastically-stretchable or deformableupper end extension 21 of the dip tube 22 through which the inlet port20 is placed in communication with the lower end portion of thecontainer so as to be capable of withdrawing substantially the entireliquid contents therefrom. An inlet valve 23 permits the flow of liquidupwardly through the inlet port 20 and prevents its downward flow fromthe pump chamber 30.

The reciprocable portion 25 of the pump here shown is exemplified by thetubular plunger, generally designated 25, and including a hollow plungerrod 26 which is received with substantial clearance in the cylinder 10,together with the anular piston 27 of relatively-greater diameter havingan outwardly and downwardly-flaring skirt 28 in operative wipingengagement with the inner wall surface of the cylinder to define avariable volume pump chamber 30 in the lower end portion of the cylinderbetween the piston 27 and the inlet port 20` in the lower end wall ofthe cylinder. The passage 29 through the plunger opens upwardlythereinto from the pump chamber 3f) into communication with otherpassages leading to the outlet or discharge orifice of the plunger, ashereinafter described.

The plunger 25 is resiliently projected upwardly on its suction strokeby the coil spring 31 which encircles the lower end extension 32 of itsplunger rod 26 and is compressed between the piston 27 and a spring seat33 jointly defined by the axially upwardly-presented ends of a series ofannularly-arranged and relatively circumferentially spaced splines 34formed integrally with and projecting radially inwardly from the innerwall of the cylidner concentrically to the inlet valve port 20. Disposedfor axial sliding movement between the respective splines 34 are thesplines or keys 35 of a peripherally-splined disc 36 projecting radiallyoutwardly beyond the base of the conical valve body 24 and preferablyafiixed thereto as an integral portion of the valve. The splines 35 thusextend radially outwardly beneath the lower convolution of the plungerspring 31, which thus serves as a stop -for limiting the unseatingmovement of the inlet valve 24.

Upward movement of the plunger on its suction stroke, under theexpansive force of the spring 31, is limited by engagement of theupwardly-directed annular shoulder or abutment 37 of the plunger with asuitable stop element such as the sealing ring 38. The sealing ring 38is secured against axial upward displacement in the cylinder byreception within the inwardly-opening groove or annular seat 39internally of the cylinder.

The plunger rod 26 extends upwardly for axial movement through thesealing ring 38 and the open upper end of the cylinder 10 for actuationin conventional manner by intermittently-applied finger pressure againstits upper end. The plunger 25 includes at its upper end agenerallyconventional plunger discharge head 40, which may tbeconstructed in a manner heretofore known and formed to provide anupwardly presented button or fingerpiece 41 adapted to receive theactuating finger pressure. In the form here shown, the plunger dischargehead40 is fabricated separately from the rest of the plunger, as anintegral plastic molding having a blind socket 42 to be fitted yover theupper end of the plunger rod 26 in snug fiuid-tight relation therewithand secured in place thereon, as `for instance by means of cooperatingsnap rings and grooves 43.

The plunger head here shown is in the form of a spray head and to thisend is formed with a restricted spray discharge orifice 45 communicatingwith a swirl chamber 46 which, in turn, is supplied with fluid through agroove 47 from the inner end portion of the socket 42. This groove orpassage 47, in turn, communicates with the axial passage 29 through theplunger. The said intercommunicating passages jointly define the plungerdischarge passage leading from the pump chamber upwardly to and throughthe discharge orifice 45.

It will be readily apparent that the inlet valve 23, in addition to itsmodes of operation as hereinafter described, also is adapted to functionin the manner of a conventional check valve, to open in response tosuction created by the up-stroke of the plunger whereby to admit liquidthrough the inlet port 20r into the pump chamber 30 and to be seated bypressure created Within the pump chamber on the compression stroke ofthe plunger.

While the function of an upper check valve may be served by therestricted orifice 45 of the spray head in a manner well known in theart, it will generally be desirable to achieve somewhat greaterefiiciency through provision of such a check valve 48, in cooperationwith the valve seat 5t) within the plunger. The stop finger 51,depending from the plunger head into the upper end of the axial plungerpassage 29, limits the unseating movement of the valve 48.

In order that the hereinafter-described interior and exterior shippingseals may be securely maintained when the pump and its associated liquidcontainer are conditioned for shipping with the plunger in itsfully-depressed condition, there may be provided any suitable means forthus releasably holding the plunger fully depressed.

The means herein illustrated for purposes of exemplication areconventional, and comprise an externallythreaded plug 55 at the base ofthe plunger head 4t)l for cooperating reception in theinternally-threaded collar 12 of the cylinder 10.

The plug 55 is also illustrated as being provided with radially andaxially-projecting annular seals 56 and 57 respectively for engagementwith cooperating sealing surfaces of the collar, all in a manner nowwell known. However, since such seals and their function are merelycumulative to the function of the exterior sealing means more fullyhereinafter described, it will be appreciated that the seals 56 and 57are merely optional.

Referring now in more detail to the particular valve actuating andsealing features constituting the subject matter of the instantinvention, it will be noted that'the inlet valve 23 is provided with anaxially upwardly-directed and substantially-rigid valve stem 58 whichprojects axially into the discharge passage 29 of the plunger, and isfreely movable in such passage through a sealing valve port 59, throughwhich it passes with sufficient clearance as to permit substantiallyunimpeded uid flow. Carried at the free end of the valve stem 58 is asealing valve 60 which is positioned for alternate seating at oppositeextremities of the plunger movement with the sealing port 59 and withthe further sealing port 61. Port 61 is spaced axially along the passagefrom the port 59 at such a distance as to cause said ports to cooperatewith the valve 60 at opposite extremities of the plunger movement, itbeing apparent that the latter is movable within predetermined limits.governed by the engagement of the plunger with the inlet valve on theone hand and by the abutting engagement between the annular plunger stopsurface 37 and sealing ring 38 on the other hand.

In order to adapt it for alternate cooperation with the specific typesof valve ports designated at 59 and 61 respectively, the valve 60` isprovided with a conical upper end portion 60a converging toward the port61 and adapted for sealing reception therein. The port 61 in the presentinstance is defined by the lower end of a sleeve 62 depending from andconstituting an integral portion of the valve seat 50, and of anelastically-expansible material such that the valve seat defined by thelower end of the sleeve 62 at port 6-1 is circumferentially expanded bysealing reception of the conical valve portion 60a. The seating pressurebetween these parts is transmitted through the valve stem to the inletvalve 23, and the oppositelydirected and elastically-expanded valveseats operate in similar manner in conjunction with their conical valveportions 6a and 24 respectively to maintain a constant resilient seatingengagement with these portions as long as the plunger is locked in itsfully-depressed position.

For cooperation with the valve port 59 (which may be seen to constitutea constriction defined by the mutuallyconverging conical passageportions 63 and 64 within the plunger passage 29), the sealing valve 60is provided with la substantially-cylindrical portion 60h proportionedfor snug frictional sealing reception in the port or constriction 59. Atapered pilot portion 60C of the sealing valve 60 extends from thecylindrical portion 60h toward the constriction 59 to guide the enlargedportion 6G17 into the constriction of port 59.

It will be apparent that the sealing valve 60 will seat in the port 59when the plunger is fully projected to the upper or outer limit of itsstroke by action of the plunger spring 31, the upward movement of thevalve 60 having been previously arrested by cooperation of the spring 31and splined disc 34. Moreover, by virtue of the relationship of thesealing valve 60 and the constricted port 59, it Vwill be apparent thatthe valve 60 may be readily assembled in operative position for movementbetween the two ports or seats 59 and 61 simply by inserting it into thelower or inner end of the plunger passage and forcing it through theconstriction 59.

In addition to its valving function, the valve 60 cooperates with theconstricted port or seat 59 to establish a frictional coupling betweenthe plunger and the inlet valve at the end of each suction stroke of theplunger, so that, at the inception of a downward or compression strokeof the plunger, its movement is frictionally transmitted to the inletvalve 23 to seat same. The frictional coupling will be disengaged bycontinued downward movement of the plunger.

A further frictional coupling between the plunger 25 and valve 23 forunseating of the conical valve portion 24, at the inception of theupward or suction stroke of the plunger from its fully-depressedposition as shown in FIGURE 2, is provided by means of a cylindricalplug 65 carried by and preferably formed integrally with the valve 23.This plug 65 is proportioned for snug frictional reception in the lowerend of the plunger passage 29 below the piston 27. This plug 65 also ispreferably provided with a conical guide portion 66 to facilitate itsentry into the passage incident to the downward movement of the plunger.Thereafter, when the plunger is released to commence its up-stroke, thefrictional coupling thus established between it and the inlet valve 23exerts an unseating force on the latter until such coupling isdisengaged by abutment of the splined disc 36 with the plunger spring.

The thrusting engagement of the valve seat 61 at the lower end of sleeve62 with the sealing valve 60 exerts a positive seating force which istransmitted to the inlet valve 24 through its stem 58. However, it maybe desirable in some instances to duplicate this seating thrust byextending the lower end of the plunger rod 26 to cause it to pressaxially against the upper face of the inlet valve disc 36 in thefully-depressed position of the plunger. In addition, it will beapparent that the relatively-thicker and heavier plunger extension 32cooperates with the relatively lighter and resiliently or elasticallyexpandable lower end of the sleeve 62 to gauge and limit the expansionof the latter by affording a positive limit for relative downwardmovement of the plunger onto the seated inlet valve 24.

It will be apparent that the several parts of the pump other than theplunger spring itself may Ireadily be formed by conventional plasticmolding processes from various plastic materials, as for instancepolyethylene, having sufficient qualities lof flexibility and elasticityto function as above described. The construction and arrangement of theinterior seals having thus been fully described, reference will now bemade in greater detail to the preferred construction and operation ofthe exterior seals.

Such exterior seals comprises the combined sealing ring and plunger stop38 which, as earlier mentioned, encircles the plunger 25 and ispositioned in the cylinder 10 within a groove 39 by which it is securedagainst substantial axial displacement when engaged by the reciprocatingplunger.

The upper end wall of the groove 39 preferably is of substantial radialextent to afford a positive limit for preventing upward displacement ofthe ring 38, and, therefore, in the preferred embodiment, is formed byan integral inwardly projecting radial rib 68 within the pump cylinderadapted for reception of the plunger with a slight clearance.

In order to adapt the ring 38 for positioning within the groove 39, thering 38 may be formed of a material such as natural rubber,polyethylene, or the like, capable of being sufficiently deformed topermit its insertion downwardly through the rib 68 and adaptedthereafter to expand outwardly into resilient sealing engagement withthe bottom of the groove 39.

The pump barrel is provided with a usual vent or opening 69 above thepiston 28 and preferably just below the ring 38 to permit the escapeback into the container of any liquid which might have :become trappedin the cylinder above the piston 27 and such as might, in the absence ofa vent, interfere with the movement of the plunger as well as causeupward leakage of liquid past the sealing ring 38. For venting theinterior of the container to the atmosphere so that it may normally besubstantially at atmospheric pressure during the pumping operation, theportion 71 of the plunger which -moves through the sealing ring 38throughout the major part of the plunger stroke in either direction, isof sufficientlyreduced diameter relative to the ring as to have a slightclearance therewith, as is apparent in FIGURE l. Accordingly, when theplunger is in various intermediate positions between the extremities ofits stroke, communication is establishedbetween the vent 69 and theatmosphere between the inner periphery of the sealing ring 38 and theplunger rod, through the open upper end of the cylinder.

At opposite axial ends of the reduced plunger portion 71, the plunger isformed with cylindrical enlargements 72 and 73 respectively positionedfor sealing reception in the ring 38 at opposite extremities of theplunger movement.

The ring 38 is adapted for limiting and sealing engagement with theplunger in the upwardly-projected position of the latter, in the mannerexemplified in FIG- URE l, in which the sealing ring is shown to beaxially compressed between the annular stop rim or ledge 37 of theplunger and the stop rib y68 within the cylinder. While the stop ring 38may assume various forms, it has been found that one suitable crosssectional shape of the ring is as illustrated, in which the sarne isprovided with radially-inner and outer pairs of relatively upwardly anddownwardly diverging conical skirts 74, 74', 75, '75 respectively,connected to each other and to the main body of the ring 38 along aradial plane midway of the axis of the ring. These radially-opposedpairs of skirts are arranged so that the radially outer peripheries ofthe skirts 75, 75 Will normally be deflected somewhat radially inwardlyby and seal against the `bottom of the groove 39, While the innerperipheries of the respective skirts 74, 74 are proportioned for sealingengagement with the respective plunger enlargements 72 and 73 and forclearance with the reduced intervening plunger portion 71. The ring alsocomprises oppositely axially-diverg ing pairs of conical skirts 76, 76and 77, 77 of which the radially outer and radially inner such skirts 76and 77 respectively are adapted for sealing engagement with I the rib 68and with the annular sealing ledge or shoulder 37 of the plunger. Thus,in the fully spring-projected position of the plunger, the sealing ring38, in addition to its function as a stop for determining such position,has both of its sealing skirts 75, 75' and also its skirt 74 inresilient radial sealing engagement with the cylinder and plungerrespectively, while its upper and lower skirts 76 and 77 are in axialsealing engagement with the stop rim 68 and stop ledge 77 respectively.Rather than form the ring with separate sets of skirts for separateradial and axial sealing engagement with the plunger, the sealing ringmay be formed to omit the skirts 76, 76', 77, 77', and to utilize theremaining skirts 74, 74' and 75, 75' for both purposes. Obviously thesealing ring is capable of other cross sectional forms as will beobvious to those skilled in the art.

The linvention in its preferred form is capable of assembly from a smallnumber of parts which, except as to the plunger spring and ball checkIvalve, are adapted to lbe molded in conventional manner of usualplastic materials.

The cylinder may be formed of a comparatively rigid plastic material andassembled to the container cap in conventional manner by pressing orswaging the rib 16 therein after insertion of the collar portion throughthe opening within the container closure. The castellated shoulder 78which is formed externally around the cylinder in accordance withconventional practice affords means for supporting the cylinder withinthe conventional tool both to withstand both axial thrust imposedthereon incident to the swaging of rib 16 and the torsional forceincident to holding the cylinder 10 against rotation where, afterassembly of the several parts, the pump plunger is locked in itsfully-depressed position by simultaneously depressing and rotating samewith its externally-threaded plug 55 engaged in the threaded collar 16.

Although various modes and orders of assembly of the pump componentswill be apparent, it may be noted by way of illustration that inletvalve 23 is capable of assembly within the cylinder merely by droppingit downwardly into the cylinder through the open upper end thereof,following which the spring 31 may similarly be dropped into positionaround the stem of the valve 23. After insertion of the stop ring 38into position, same may be resiliently expanded to permit insertion ofthe plunger. The flexible piston skirt will at the same time be radiallycompressed to pass through the ring. Even though the splines or keys maynot initially have registered with the spaces between the splines 34 ofthe spring seat, the saidsplines will nevertheless be brought intoregistry with each other by rotation of the plunger, which will betransmitted through the frictional connections established between theplunger and inlet valve at either extremity of the plunger movement.

Formation of the internal stop rib 68 within the cylinder is preferablydeferred until after insertion of the plunger. The plunger components,namely the ball check valve 48 and plunger discharge head 40, may beassembled after the assembly of the plunger and cylinder, and theswaging of the stop rib 68.

OPERATION Plzmger fully depressed Kand locked When the dispenser of theinvention is delivered to the ultimate consumer, it will in mostinstances be applied to the container ofv liquid to be dispensed therebywith the plunger either in its fully-depressed position, as in FIG- URE2, or in its fully-projected position, as in FIGURE 1. In either event,suitable shipping seals will have been established and maintainedforpreventing loss or leakage of the liquid both through the pump dischargepassage of the plunger and between the plunger and cylinder walls.

Assuming that the dispenser is delivered with the plunger locked in itsfully-depressed position, as in FIGURE 2, the discharge of liquidthrough the internal pump passages will have been barred by successiveinternal seals. To this end, it will be seen that the inlet valve cone24 is thrust against its valve seat 21 around the inlet port 20 by thelower end of the plunger 25. Plunger passage 29, in turn, is sealed byfrictional reception of the sealing plug portion 65 of the valve, whilethe sealing valve 60 carried at the upper end of the plunger stem issimilarly in axially-thrusting sealing relation with the outlet valveport defined by the depending sleeve 62. The seats around the ports 61and 2) respectively are elastically expanded by the cooperating conicalvalve portions a and 24 so that the elastic contracting tendency ofthese ports, acting on the conical surfaces 60a and 24 maintains aconstant resilient thrusting and seating force on both valve portions60a and 24 against their respective ports.

Thus, liquid normally is unable even to enter the pump chamber 30through the inlet port 20 prior to the initial use of the pump. However,where, after its initial use, the pump plunger is again locked in itsfully-depressed position, any liquid then contained Within the chamber30 is barred from entry into the lower end of the plunger by means ofthe sealing plug 65. Also, upward movement of liquid through the plungeris barred by the seated relation of the valve portion 60a in port 61.

In addition to the internal seals thus established in thefully-depressed position of the plunger, the enlargement or upper valveportion 72 of the plunger is at this time received within the stop ring38 to resiliently compress the said stop ring radially between theopposed faces of the enlargement 72 and the bottom of groove 39. Thus,any liquid which may have entered the cylinder through the vent 69 orhave leaked upwardly past the plunger skirt or piston 28, will beconfined against escape past the sealing ring 38 which thus coacts withthe plunger and pump cylinder to define an effective external seal.

Pumping action When the plunger and plunger head are rotated to releasethe threads 55 from the internally-threaded collal 12 of the plungercylinder, the plunger spring 31 immediately expands to project theplunger upwardly and outwardly on its suction stroke. At the inceptionof the suction stroke, the frictional coupling provided by theinterengaged plug portion 65 of the inlet valve and the plunger exerts apositive unseating force on the inlet valve to free the latter in theevent it should have become stuck in place. This function is augmentedby the resiliently-contracting tendency of the expanded valve seat 21.Similarly, the somewhat expanded valve seat of the port 61 and thesealing valve 60a cooperate in a manner to free themselves. As the inletvalve reaches the limit of its unseating movement, as determined byaxial abutment of its disclike portion 30 with the lower coil of spring31, continued upward movement of the plunger disengages it from the plug65 while simultaneously unseating the valve portion 60a from port 61.Thereafter, continued upward movement of the plunger, with the inletvalve 23 unseated, causes liquid to be drawn upwardly through the diptube 22 from the container and through the inlet port 20 into the pumpchamber 30.

Moreover, in this upward or suction stroke of the plunger, the reduceddiameter plunger portion 71 moves freely and with clearance through thesealing ring 38, during which time air from the atmosphere is free toseep downwardly between the ring and the open end of the pump cylinderand thence into the container through the vent 69 to replace liquidwithdrawn by the pumping action.

Throughout the upward or suction stroke of the plunger, the upper pumpvalve 48 will normally be seated to produce a relatively-reducedpressure or suction within the pump chamber 30; or if the ball valve 48is omitted, the discharge orifice 45 may be proportioned to produce asimilar though less efficient function.

The upward unseating movement lof the inlet Valve 23 will have beenarrested by the plunger spring, during the early portion of the suctionstroke.

As the plunger nears the upper end or limit of its suction stroke, thesealing valve 16, being restrained against upward movement by itsconnection to the inlet valve, will be frictionally received and seatedin sealing relation within the constricted port 59 of the plunger, asshown in FIGURE l. The suction st-roke of the plunger will then beterminated by abutment between the plunger stop ledge or shoulder 37 andthe Vsealing ring 38. At this time, pump chamber 30 communicates freelywith the container through the inlet port and tube 22, but the plungerpassage is firmly sealed by seating of the valve 60 in port 59 of theplunger. At this time, an external seal is provided by the interengagedplunger ledge 37 and sealing ring 38 by virtue both of the axial sealingengagement aforementioned, as well :as of the radial sealing engagementof the plunger enlargement 73 Within the sealing ring.

Thus, the plunger cooperates with the sealing ring in the manner of aslide valve to seal off the vent opening 78 from communication with theatmosphere in either the fully-projected or fully-depressed positions ofthe plunger, while permitting such communication during normal operationof the plunger.

On the inception of each downward or compression stroke of the 4plungerby finger pressure on the plunger head, the frictional gripping orclutching engagement between the plunger constriction or valve seat 59and its associated sealing valve 60 transmits a frictional seatingthrlust from the plunger to the inlet valve 23. When the inlet valve isseated and no longer free to move with the plunger, continued plungermovement will afford a .positive unseating of the sealing valve 60.

The -plunger may obviously be reciprocated repeatedly to eject thedesired amount of liquid, following which it may either be left in itsfully-projected position, under the action of the plunger spring 31, or,if desired, may be locked in its fully-depressed position, in the mannershown in FIGURE 2. In either event, it will be quite apparent that theactuation of the inlet valve 23 and its associated sealing valve 60 willoccur independently of gravity, through the transmission of frictionalseating and unsealing forces from the plunger. If it is desired to freethe pump structure completely from the action of gravity, the ball valve48 may be eliminated and its function taken over, for instance, by asufficiently-constricted discharge orifice 45 ofthe plunger head or `bya spring-loaded valve. Also, the action of the sealing valve or plug 65will similarly be controlled by the plunger position independently ofgravity. Thus, the plunger will be effectively sealed internally ineither its fully-projected or fully-depressed position and will be fullysealed externally by the coaction between the plunger rod and thesealing ring in the manner of a slide valve.

Having thus described my invention, I claim:

1. In a reciprocating liquid pump, including a pump cylinder having aninlet port through one axial end thereof, an inlet valve disposed insaid cylinder for axial movement within pre-determined limits into andfrom seating relation with said inlet port, and a plunger disposed foraxial movement within pre-determined limits in said cylinder on suctionand compression strokes respectively away from and toward said inletport, said plunger being provided with an axial discharge passagetherethrough; the improvements comprising:

(A) a pair of relatively axially-spaced sealing valve seats within saidplunger and around said passage, and respectively defining ports ofsmaller cross sectional area than the discharge passage;

(B) a substantially-rigid valve stem afiixed to said in- -let valve andextending axially therefrom into said passage for relative axialmovement therein; and

(C) a sealing valve fixed to said valve stem within the passage forrelative movement between said sealing valve seats and for alternateseating engagement with said sealing valve seats at opposite limits ofthe movement of the plunger.

2. In a reciprocating liquid pump as defined in claim 1, the furtherimprovement comprising means for limiting the unseating lmovement ofsaid inlet valve, the seating of said inlet valve determining the limitof its seating movement.

3. In a reciprocating liquid pump as defined in claim 1, the furtherimprovement wherein said sealing valve seats are located relativelyadjacent and remote from said inlet port respectively, the valve stembeing disposed for free movement through the port defined by saidrelativelyadjacent valve seat, friction clutch means on said valve stemnormally positioned for relative movement between said sealing valveseats and proportioned for axial reception in and frictional radialengagement with said relativly-adjacent valve seat at the limit of eachsuction stroke of the -plunger to transmit a yieldable axial seatingforce from the plunger of the inlet valve on the inception of eachcompression stroke of the plunger.

4. The combination defined in claim 3, in which said friction clutchmeans comprises the sealing valve, said sealing valve being proportionedfor seating and sealing radially against the inner periphery of saidadjacent sealing valve seat while frictionally engaging same.

5. The combination defined in claim 4, in which said relatively-adjacentsealing valve seat is defined by oppositely-directed generally-conicalsurfaces diverging toward each other to define a port the innerperiphery of which is proportioned for frictional sealing engagementwith said sealing valve.

6. The combination defined in claim 4, in which said relatively-remotesealing valve seat is positioned for positive axial thrusting engagementwith said sealing valve to transmit a positive seating force throughsaid sealing valve and said valve stem to the inlet valve as the plungerapproaches the limit of its movement toward the inlet valve, and meansfor releasably interlocking said plunger to said cylinder to secure theplunger at the said lastmentioned limit of its movement.

7. The combination defined in claim 6, in which said relatively-remotesealing valve seat is directed axially toward said sealing valve forpositive seating abutment therewith.

8. In a reciprocating liquid pump as defined in claim 1, the furtherimprovement in accordance with which said sealing valve is proportionedfor axial movement completely through one of said sealing valve seats tofacilitate assembly of the sealing valve and plunger, and for sealingand frictional engagement with the inner periphery of said one sealingvalve seat during its passage therethrough.

9. In a liquid dispensing pump as defined in claim 1, the furtherimprovement in which said plunger includes a third downwardly-directedannular sealing valve seat, a second sealing valve being carried by saidvalve stem in position to seat against said third sealing valve seatnear the limit of the compression stroke of the plunger.

10. In a liquid dispensing pump as deiined in claim 1, the furtherfeature in which said inlet valve comprises a plug directed axiallytoward said plunger and positioned for snug liquit-tight reception insaid lplunger discharge passage near the limit of the compression strokeof said plunger.

11. In a liquid dispensing pump as dened in claim 10, the furtherimprovement in which said sealing plug is frictionally received in saidplunger discharge passage to transmit a yielding rictional unseatingforce from the plunger to the inlet valve on retraction of the plungerfrom its position at the limit of its movement toward the v inlet port.

12. In a reciprocating liquid pump as defined in claim 11, the furtherimprovement in accordance with which said inlet port and saidrelatively-remote sealing seat are defined by yradially expansibleannular means, said inlet valve and said sealing valve having conicalportions for simultaneous sealing reception in the said inlet port andrelatively-remote sealing seat, whereby the elastic contacting tendencyof the respectively-annular means will maintain a constant resilientseating thrust of said annular means against the respective conicalportions.

13. A fluid dispensing pump as defined in claim 1, in which saidcylinder is encircled internally with a radial groove adjacent its axialend remote from said inlet port and is open through said axial end, saidplunger including an annular stop shoulder directed toward said openend, said cylinder being formed with a vent opening through its sidewall on the side of said groove remote from the open end, an annularplunger stop and sealing ring received in said groove and encirclingsaid plunger, said ring being resistant to axial compression for axialsealing abutment with said plunger shoulder and with one axial end ofthe groove to limit the plunger movement away from said inlet port, saidplunger having a portion of reduced diameter positioned for movementthrough said element to permit flow of fluid between said plunger andsaid ring during the major -portion of its stroke, and portions ofrelatively-larger diameter at opposite axial ends of said reduceddiameter portion for sealing reception in said ring at the oppositelimits of the plunger movement.

14. A fluid dispensing pump as deined in claim 13, in which said ring isresiliently compressible radially between said plunger and saidcylinder.

15. In a reciprocating liquid pump, including a pum-p cylinder having aninlet port through one axial end thereof, an inlet valve disposed insaid cylinder for axial movement within pre-determined limits into andfrom seating relation with said inlet port, and a plunger disposed foraxial movement within pre-determined limits in said cylinder on suctionand compression strokes respectively away from and toward said inletport, said plunger being provided with an axial discharge passagetherethrough; the improvements comprising:

(A) a pair of relatively axially spaced sealing valve seats in saidplunger along said passage;

(B) and a sealing Valve supported from said inlet valve within saidpassage for alternate seating engagement with said sealing valve seatsat opposite limits of the movement of the plunger.

16. In a reciprocating liquid pump as dened in claim 15, the improvementin accordance with which said sealing valve includes a plug proportionfor functional sealing reception in said discharge passage.

References Cited UNITED STATES PATENTS 3,228,347 1/1966 Corsette..103-178 FOREIGN PATENTS 9,599 5/1907 Denmark.

HENRY F. RADUAZO, Primary Examiner.

1. IN A RECIPROCATING LIQUID PUMP, INCLUDING A PUMP CYLINDER HAVING ANINLET PORT THROUGH ONE AXIAL END THEREOF, AN INLET VALVE DISPOSED INSAID CYLINDER FOR AXIAL MOVEMENT WITHIN PRE-DETERMINED LIMITS INTO ANDFROM SEATING RELATION WITH SAID INLET PORT, AND A PLUNGER DISPOSED FORAXIAL MOVEMENT WITHIN PRE-DETERMINED LIMITS IN SAID CYLINDER ON SUCTIONAND COMPRESSION STROKES RESPECTIVELY AWAY FROM AND TOWARD SAID INLETPORT, SAID PLUNGER BEING PROVIDED WITH AN AXIAL DISCHARGE PASSAGETHERETHROUGH; THE IMPROVEMENTS COMPRISING: (A) A PAIR OF RELATIVELYAXIALLY-SPACED SEALING VALVE SEATS WITHIN SAID PLUNGER AND AROUND SAIDPASSAGE, AND RESPECTIVELY DEFINING PORTS OF SMALLER CROSS SECTIONAL AREATHAN THE DISCHARGE PASSAGE; (B) A SUBSTANTIALLY-RIGID VALVE STEM AFFIXEDTO SAID INLET VALVE AND EXTENDING AXIALLY THEREFROM INTO SAID PASSAGEFOR RELATIVE AXIAL MOVEMENT THEREIN; AND (C) A SEALING VALVE FIXED TOSAID VALVE STEM WITHIN THE PASSAGE FOR RELATIVE MOVEMENT BETWEEN SAIDSEALING VALVE SEATS AND FOR ALTERNATE SEATING ENGAGEMENT WITH SAIDSEALING VALVE SEATS AT OPPOSITE LIMITS OF THE MOVEMENT OF THE PLUNGER.